laminar flow heat transfer enhancement...

LAMINAR FLOW HEAT TRANSFER ENHANCEMENT IN MULTY-START

SPIRALLY CORRUGATED TUBES

ZAID SATTAR KAREEM

A thesis submitted in fulfilment of the

requirements for the award of the degree of

Doctor of Engineering (Mechanical Engineering)

Faculty of Mechanical Engineering

Universiti Teknologi Malaysia

AUGUST 2016

iii

ACKNOWLEDGEMENT

Foremost, I say “Alhamdulillah” for the first of godsends and providing me the

strength, patience, courage, and determination in completing this work. All graces and

thanks belong to Almighty Allah Subhanahu Wa-Ta'ala (S.W.T) and May blessings and

peace be upon our prophet Mohammad (S.A.A.W).

Many thanks and Gratitude goes to my supervisor Assoc. Prof. Dr. Tholudin Mat

Lazim, and to my co-supervisors Prof. Dr. Mohd Nazri Mohd Jaafar and Prof. Dr. Ir.

Shahrir Abdullah for their incredible guidance. The successful completion of this work

is due to the support of the supervision members.

I am also indebted to Universiti Teknologi Malaysia (UTM) for their help and

care. The appreciation should forward to University Kebangsaan Malaysia, NGVD

center for allowing me to use their resources.

My fellow postgraduate students should also be recognized for their support. My

sincere appreciation also extends to all my colleagues and others who have provided

assistance at various occasions. Their views and tips are useful indeed. Unfortunately, it

is not possible to list all of them in this limited space. I am grateful to all my family

members.

iv

ABSTRACT

Heat transfer plays an important role in many aspects of human life, especially

the forced convection type. Hence, it has become very important to invest resources and

efforts in this vital field to make some difference. Recently, the trend of using compact

heat transport devices is of great interest to obtain an efficient, low cost and small size

product which requires less production time with fewer efforts. Employing of artificial

roughness, such as corrugation, for heat transfer enhancement in heat exchanger and

other industrial thermal devices have shown promising results, with good performance

reliability at lower cost. Therefore, the current study aimed to investigate experimentally

and numerically the heat transfer enhancement and pressure drop increase in tubes with

a superior type of corrugation i.e. the spiral corrugation. The flow of ionised water as

working fluid in tubes at low Reynolds number was constructed to investigate the

laminar flow regime of 100≤ Re≤1300. Five spirally corrugated tubes and one smooth

tube under constant wall heat flux boundary condition with various thermo-physical

properties was investigated through experimental test and computational fluid dynamics

simulation. Different corrugation parameters, such as corrugation height to diameter and

corrugation pitch to diameter ratios were studied in different corrugated tube sizes. The

results showed that the severity index, which combines the effect of both corrugation

height and pitch, has great effects on heat transfer rate, friction factor, and thermal

performance of the flow inside spirally corrugated tubes. The heat transfer enhancement

was in the range of 1.3-2 compared to a smooth tube, accompanied with an increase in

friction factor in the range 1.1-1.9. The thermal performance range was found to be

improved by 1.2-2.08 times. The heat transfer and friction factor correlation are

proposed.

v

ABSTRAK

Pemindahan haba memainkan peranan penting dalam banyak aspek kehidupan

manusia, terutamanya jenis pemindahan haba olakan paksa. Oleh itu, menjadi sangat penting

untuk melabur dalam sumber dan tenaga usaha dalam bidang yang amat perlu ini untuk

menghasilkan sesuatu perubahan yang ketara. Kebelakangan ini, penggunaan alat

pengangkutan haba yang padat telah menjadi satu polar yang sangat menarik untuk

meningkatkan kecekapan, menurunkan kos dan saiz produk sehingga boleh mengurangkan

masa pengeluaran dan daya usaha. Penggunaan kekasaran tiruan, seperti permukaan kerut-

beralun, untuk peningkatan pemindahan haba dalam penukar haba dan lain-lain peranti terma

skala industri telah menampakkan kejayaan, dengan prestasi kebolehpercayaan yang baik dan

kos yang lebih efektif. Oleh itu, kajian ini bertujuan untuk menyiasat melalui kaedah ujikaji

dan berangka, peningkatan pemindahan haba dan pertambahan penurunan tekanan dalam tiub

yang mempunyai kerut-beralun yang lebih unggul iaitu kerut-beralun pilin. Aliran air terion

sebagai bendalir bekerja dalam tiub pada nombor Reynolds yang rendah telah dibina untuk

menyiasat rejim aliran lamina yang mempunyai 100≤ Re≤1300. Lima tiub kerut-beralun pilin

dan satu tiub licin di bawah keadaan sempadan fluks haba dinding pemalar dengan pelbagai

sifat terma fizik disiasat melalui ujian ujikaji dan simulasi perkomputeran dinamik bendalir.

Berbagai parameter kerut-beralun, seperti nisbah ketinggian kerut-beralun kepada garis pusat

dan nisbah jarak alun kepada garis pusat dikaji dalam berbagai saiz tiub kerut-beralun. Hasil

kajian menunjukkan bahawa indeks keamatan, yang menggabungkan kesan kedua-dua

ketinggian kerut-beralun dan jarak alun, mempunyai kesan yang besar pada kadar

pemindahan haba, faktor geseran, dan prestasi terma untuk aliran di dalam tiub kerut-beralun

pilin. Peningkatan pemindahan haba adalah dalam julat 1.3-2 berbanding dengan tiub licin,

dengan penambahan dalam faktor geseran dalam julat 1.1-1.9. Julat prestasi terma telah dapat

diperbaiki sebanyak 1.2-1.9 kali ganda. Sekaitan pemindahan haba dan sekaitan faktor

geseran telah dicadangkan.

vi

TABLE OF CONTENTS

CHAPTER TITLE PAGE

DECLARATION ii

ACKNOWLEDGEMENT iii

ABSTRACT iv

ABSTRAK v

TABLE OF CONTENTS vi

LIST OF TABLES x

LIST OF FIGURES xi

LIST OF ABBREVIATIONS xvii

LIST OF SYMBOLS xviii

LIST OF APPENDICES xx

1 INTRODUCTION 1

1.1 Problem background 1

1.2 Problem statement 5

1.3 Research hypothesis 6

1.4 Research questions 6

1.5 Objectives 7

1.6 Scope of research 8

1.7 Significance and contributions of this study 8

1.8 Organization of the thesis 9

vii

2 LITERATURE REVIEW 11

2.1 Introduction 11

2.2 Active method 12

2.3 Passive methods 14

2.3.1 Twisted tape 15

2.3.2 Coiled wires 17

2.3.3 Swirl generators 19

2.3.4 Conical ring 21

2.3.5 Ribs 22

2.3.6 Dimples 23

2.3.7 Grooves 25

2.3.8 Additives (nanofluid) 27

2.3.9 Miscellaneous techniques 29

2.3.10 Corrugations 30

2.3.11 Experimental studies on corrugation 31

2.3.11.1 Laminar flow 31

2.3.11.2 Turbulent flow 36

2.3.11.3 Laminar to turbulent 50

2.3.12 Numerical studies on corrugation 56

2.3.12.1 Laminar flow 56

2.3.12.2 Turbulent flow 58

2.3.12.3 Laminar to turbulent 62

2.3.13 Miscellaneous corrugation studies 62

2.4 Summary 63

3 EXPERIMENTAL METHODOLOGY 65

3.1 Introduction 65

3.2 Characteristics of spirally corrugated tubes 66

3.3 Corrugation height and pitch 69

3.4 Heat transfer and pressure losses measurement 70

3.4.1 Experimental set up 70

viii

3.4.2 Experimental procedures 74

3.4.3 The determination of heat transfer and friction

factor 75

3.5 Calibration of the instruments 77

3.5.1 Calibration of thermocouples 78

3.5.2 Calibration of pressure transducers 79

3.5.3 Calibration of water flow meters 80

4 MATHEMATICAL MODELLING 82

4.1 Introduction 82

4.2 Numerical modelling 82

4.2.1 Geometry of simulated tubes 83

4.2.2 Governing equations 87

4.2.2.1 Continuity and momentum equations 87

4.2.2.2 Energy equation 88

4.3 Meshing Strategy 88

4.2.3 Mesh quality 89

4.2.4 Grid density 90

4.4 Boundary conditions and assumptions 93

4.5 Heat transfer determination 93

4.6 CFD Verification 95

4.6.1 Solution algorithm 95

4.6.2 Solution algorithm and solution method 96

4.6.3 Residual convergence 96

4.6.4 Grid convergence index 98

4.7 CFD Validations 104

4.7.1 Heat transfer validation 105

4.7.2 Friction factor validation 106

4.9 Summary 108

ix

5 RESULTS AND DISCUSSION 110

5.1 Introduction 110

5.2 Effect of corrugation profile on heat transfer 110

5.3 Friction factor results 134

5.4 Effect of corrugation height on heat transfer 139

5.5 The effect of corrugation pitch on heat transfer 144

5.6 Number of start effect on heat transfer 146

5.7 The effect of severity index on heat transfer 148

5.8 Effect of number of start on temperature 152

5.9 Effect of number of start on pressure drop 154

5.10 Effect of number of start on flow pattern 157

5.11 Nusselt Number and friction factor enhancement

Ratios 163

5.12 Thermal performance factor 169

5.13 Correlations 173

5.13.1 Nusselt number correlation 173

5.13.2 Friction factor correlation 175

6 CONCLUSIONS AND RECOMMENDATION 178

6.1 Conclusions 178

6.2 Recommendations for further study 180

6.3 Main contributions 181

REFERENCES 183

Appendix A-C 201-214

x

LIST OF TABLES

TABLE NO. TITLE PAGE

2.1 Summary of experimental studies concerned with corrugation

for laminar flow 32


for turbulent flow 36


for laminar-turbulent flow 51

2.4 Summary of numerical and analytical studies concerned with

corrugation for laminar flow 56

2.5 Summary of numerical and analytical studies concerned with

corrugation for turbulent flow 58

3.1 Tubes characteristics for number of start N=3 67

3.2 The accuracy of instruments and sensors 77

4.1 Characteristics of simulated tubes 83

4.2 GCIs of the case N=2, Re=100 and φ=0.631×10-3

104

5.1 Constant values of A and B of eq. (5.6) 173

5.2 Constant values m and n of eq. (5.8) 176

xi

LIST OF FIGURES

FIGURE NO. TITLE PAGE

1.1 Publications regarding the corrugation in heat transfer

enhancement 4

3.1 Spirally corrugated tubes configurations 66

3.2 Corrugated tube characteristics 68

3.3 The schematic diagram of experimental set up 71

3.4 The experimental rig 72

3.5 Thermocouples arrangement on the test pipe 73

3.6 Thermocouples holes 73

3.7 Calibration of thermocouples 79

3.8 Calibration of pressure transducer 80

4.1 Two-start geometry of the numerical model 85

4.2 Three-start geometry of the experimental and numerical

model 85

4.3 Four-start geometry of the numerical model 86

4.4 Five-start geometry of the numerical model 86

4.5 Mesh model of the two-start tube 91

4.6 Mesh model of the three-start tube 92

4.7 Mesh model of the four-start tube 92

4.8 Mesh model of the five-start tube 92

4.9 Residual convergence 97

4.10 Comparison of the measured and numerical Nusselt num-

ber of water with the Shah equation 105

xii

4.11 Comparison of the measured and numerical friction fac-

tor with those determined by equation 4.27 107

5.1 Numerical Nusselt number numerical data along the tube for

N=2, Re=100 112


N=2, Re=400 112


N=2, Re=700 113


N=2, Re=1000 113


N=2, Re=1300 114

5.6 Nusselt number comparison of numerical and experimental

data along the tube for N=3, Re=100 115










N=4, Re=100 118


N=4, Re=400 118


N=4, Re=700 119


N=4, Re=1000 119


N=4, Re=1300 120


N=5, Re=100 120


N=5, Re=400 121


N=5, Re=700 121

xiii


N=5, Re=1000 122


N=5, Re=1300 122

5.21 Average Nusselt number versus Reynolds number for N=2 124




5.25 Heat transfer rate versus Reynolds number for N=2 126




5.29 Average Nusselt number versus Reynolds number for

φ=0.631×10-3

129


φ=890.0×10-3

129


φ=29011×10-3

130


φ=19500×10-3

130


φ=3.857×10-3

131

5.34 Average Nusselt number versus Severity index for N=2 132




5.38 Friction factor versus Reynolds number for N=2 135

5.39 Friction factor comparison of numerical and experimental

results at N=3 and for different values of severity index 135



5.42 Friction factor versus Severity index for N=2 137



xiv


5.46 Temperature contour of Tube no. 6 of φ = 0.631×10-3

140


140


141


141

5.50 Temperature contour and vector of Tube no. 10 of

φ = 3.857×10-3

142

5.51 Velocity field of Tube no. 9 of φ = 2.588×10-3

143

5.52 Vorticity magnitude contour of Tube no. 6 of φ = 0.631×10-3

144

5.53 Streamline of Tube no. 8 of φ = 1.822×10-3

145

5.54 Pressure field of Tube no. 4 of φ = 2.588×10-3

146


147


147


148

5.58 Velocity vector (coloured by temperature values) of

Tube no. 10, with φ=3.857×10-3

149


Tube no. 9, with φ=2.588×10-3

149


Tube no. 8, with φ=1.822×10-3

150


Tube no. 7, with φ=0.898×10-3

150


Tube no. 6, with φ=0.631×10-3

151

5.63 Temperature contour of N=2 152




5.67 Pressure contour of N=2 155




5.71 Velocity vector of N=2 157

xv




5.75 Vorticity magnitude of N=2 159




5.79 Velocity contour of N=2 161




5.83 Friction factor enhancement ratios versus Reynolds number

for different severity index for N=2 164







5.87 Nusselt number enhancement ratios versus Reynolds number








5.91 Thermal performance factor versus Reynolds number of N=2

and for different severity index 170







xvi

5.95 The comparison of the Nusselt number with the Nusselt

number correlation 5.6 175

5.96 The comparison of the Friction factor with the Friction factor

correlation 5.8 177

xvii

LIST OF ABBREVIATIONS

C/W - Twisted tape clearance ratios

CFD - Computational fluid dynamics

CITSG - Conical injector type swirl generator

CR - Conical-ring

DDIR - Discrete double incline ribs

DR - Divergent ring

DWs - Delta-winglet type vortex generator

e/D - Heat capacity of the fluid, kJ/kg oC

FEM - Finite element method

FVM - Finite volume method

Fw - Wave factor

MF - Mass flux

OHP - Oscillating heat pipe

p/D - Diameter of the tube, m

PCR - Perforated conical-ring

PR - Pitch ratio

TET - Twisted elliptical tube

TT - Twisted tape

WVG - Winglet type vortex generator

Y/W - Twisted tape twist ratios

xviii

LIST OF SYMBOLS

A - Surface area, m2

Cp - Heat capacity of the fluid, kJ/kg oC

D - Diameter of the tube, m

e - Corrugation height

Gz - Graetz number

L - Length of the tube, m

k - Thermal conductivity, W/m·K

H - Heat transfer coefficient, W/m2·K

N - Number of start riding

Nu - Nusselt number

P - Pressure, Pascal

p - Corrugation Pitch

Pr - Prandtl number

Pe - Peclet number

Re - Reynold number

T - Temperature, K

t - Time, s

u - Velocity, m/s

q - Heat flux at the wall, W/m2

xix

GREEK LETTER

µ - Dynamic viscosity of the fluid, kg·m/s2

ρ - Density of the material, kg/m3

η - Thermal efficiency

φ - Severity Index

SUBSCRIPT SCRIPT

B - Bulk

b - Bore

en - Envelope

n - Nominal

x - Local

xx

LIST OF APPENDICES

APPENDIX TITLE PAGE

A Result of numerical local Nusselt number 201

B Result of numerical friction factor 212

C Experimental uncertainties 214

1

CHAPTER 1

INTRODUCTION

1.1. Problem Background

Heat transfer is the exchange of thermal energy between physical systems,

depending on the temperature, by dissipating heat. The fundamental modes of heat

transfer are conduction, convection and radiation.

Heat transfer always occurs from a region of high temperature to another

region of lower temperature. Heat transfer changes the internal energy of both

systems involved according to the First Law of Thermodynamics.

The flow of fluid may be forced by external processes, or sometimes (in

gravitational fields) by buoyancy forces caused when thermal energy expands the

fluid (for example in a fire plume), thus influencing its own transfer. The latter

process is often called "natural convection". All convective processes also move heat

partly by diffusion, as well. Another form of convection is forced convection. In this

case the fluid is forced to flow by use of a pump, fan or other mechanical means.

2

Convective heat transfer, or convection, is the transfer of heat from one place

to another by the movement of fluids, a process that is essentially the transfer of heat

via mass transfer. Bulk motion of fluid enhances heat transfer in many physical

situations, such as (for example) between a solid surface and the fluid. Convection is

usually the dominant form of heat transfer in liquids and gases. Although sometimes

discussed as a third method of heat transfer, convection is usually used to describe

the combined effects of heat conduction within the fluid (diffusion) and heat

transference by bulk fluid flow streaming.

The heat transfer is a very interesting field for economical, functional and

environmental reasons; it is almost related to each aspect of human lives. Therefore,

the enhancement of such field is quite essential, especially the forced convective heat

transfer field. The conversion and utilization of energy in industrial, commercial, and

domestic applications involve heat exchange processes. Some common examples are

steam generation and condensation in power and cogeneration plants; sensible

heating and cooling of viscous media in thermal processing of chemical,

pharmaceutical, and agricultural products, refrigerant evaporation and condensation

in air conditioning and refrigeration system, gas flow heating in manufacturing and

waste-heat recovery; air and liquid cooling of engine and turbo-machinery systems,

and cooling of electrical machines and electronic devices. Improved heat exchange,

over and above that in the usual or standard practice, can significantly improve the

thermal efficiency in such applications as well as the economics of their design and

operation

The engineering cognizance of the need to increase the thermal performance

of heat exchangers, thereby effecting energy, material and cost savings as well as

mitigation of environmental degradation had led to the development and use of many

heat transfer enhancement techniques. These methods have in the past been referred

to variously as augmentation and intensification. One of the popular ways to enhance

heat transfer which is recently of interests is using artificial surface roughness, ribs,

grooves and corrugations. Spirally corrugated surface hold the promise of enhancing

3

the heat transfer in tubes and, they are one of the most cost-effective enhancement

methods.

Basically, there are two different methods to increase the rate of heat

transferred and both of them are based on an enhanced heat transfer surface

geometry to provide a higher thermal performance. One is the active method and the

other is the passive method. The active technique requires external forces and the

passive technique requires special surface geometries or fluid additives. The

motivation behind this activity includes the desire to produce more effective heat

exchangers and heat transfer enhancement in many other industrial applications. The

ultimate objectives being to provide energy, material, and economic savings for the

users of enhanced heat transfer technology.

Setting up a periodic disturbance along the streamwise is a favorable way to

enhance the heat transfer in forced convection due to its simplicity and effectiveness

as Adachi and Uehara reported [1]. This kind of periodical retardation plays a vital

rule in the enhancement process by breaking the thermal boundary layer and distorts

the temperature field of the fluid flowing inside the tube; hence it will minimize the

resistance or the reluctance to the heat transfer. This mechanism is widely mentioned

and cited by researches as it clearly described and reviewed in Chapter 2.

Corrugation helps on increases heat transfer enhancement due to the presence

of secondary movements of the fluid adjacent to the wall. Unfortunately, in spite of

the importance of the corrugation in various industrial applications, there is not

enough publications concerning the corrugation employment in heat transfer

enhancement. Only recently, the employing of corrugation for the enhancement of

heat transfer has become interesting because it has the combined merits of extended

surfaces, turbulators and roughness as shown in Figure 1.1.

4

Figure 1.1 Publications regarding the corrugation in heat transfer enhancement [1]

Therefore, the emphasis was given in this investigation research to the use of

the spiral corrugation in heat transfer enhancement.

In the last few years, the attention was given to the importance of using

corrugation in the heat transfer enhancement due to the mentioned merits. In

addition, the main functions of corrugation are to promote the secondary

recirculation flow by inducing radial velocity components, mixing the flow layers

and finally, increasing the wet perimeter with holding the throat cross-section area

constant.

There is enough number of investigators whom tried to study the heat transfer

enhancement in both ways, experimentally and numerically. A different corrugation

profiles and arrangement were employed. Many fluids were tested inside various

tube arrangements. But yet, the studies concerning the employing of both

experimental and numerical techniques for the determination of thermal performance

5

of spirally corrugated tubes for the flow of water at low Reynolds number are limited

in spite of the thrust for a smaller size, cost effective thermal transport devices [2]. In

addition, the traditional corrugation profile was also used over and over, and the

creativity regarding the corrugation profile and its effect was completely neglected.

1.2. Problem Statement

As it is commonly known, energy resources is exhausting at a tremendous

rate; hence, it has become important to improve the heat transfer characteristics of

tubes in view of the energy situation and to avoid the issues of imminent energy lack

with suitable and well functional precautions. The passive heat transfer enhancement

basically based on the adopting of many tools that induces a swirl and vorticities at

the secondary flow region, which mixed the fluid layers and increasing the surface

area. However, the passive technique involving so many ways like twisted tapes,

fins, ribs, rough surface, additives, extended surfaces, wire coil insert and

corrugations. Corrugated tubes are a type of enhanced heat transfer tool which has

become very interesting in the past few years.

Adopting a disturbance source in the flow direction is a preferred method for

the heat transfer enhancement. Setting up a disturbance promoter, which periodically

gags the flow along the streamwise to improve the heat exchange performance is a

common technique for the interrupting of the thermal boundary layer and mixing the

flow.

The main functions of corrugation are to promote the secondary recirculation

flow by inducing radial velocity components, mixing the flow layers and finally,

increasing the wet perimeter with holding the throat cross– section area constant,

6

which leads to increases the convective surface area. Therefore, it was extensively

used in modern heat exchangers and other heat transport devices. Especially in the

food industry, where the flow is should be at low Reynolds number. Hence, this kind

of tube would be helpful in the heat treatment process of juices flowing in tubes. It

will give good results with minimum requirements. Spiral corrugation increases heat

transfer enhancement due to the presence of secondary movements of the fluid

adjacent to the wall. Therefore, the emphasis was given to the use of corrugation in

heat transfer enhancement.

1.3. Research Hypothesis

The primary flow of fluid in tube with spiral corrugated surface extension

induced a secondary flow inside the corrugation. This secondary flow is most

probably of the vortex swirl flow type. The interaction of primary pipe flow and the

swirl secondary flow will produce a unique flow pattern. This unique flow pattern

which can be studied using high fidelity computational fluid dynamics (CFD)

techniques could be deduced in term of the heat transfer performance.

1.4. Research Questions

a) How corrugation height to diameter (e/d) affect heat transfer

enhancement?

b) What are the effects of corrugation pitch to diameter (p/d) on heat

transfer enhancement?

c) Does the number of corrugation (N) affect the heat transfer

enhancement?

7

d) What is the mechanism that are heat transfers enhancement in spirally

corrugated tubes?

e) Can this mechanism be studied effectively using CFD simulation?

1.5. Objectives

The main objective of this study to determine the optimum corrugation of

spirally corrugated tube with highest heat transfer enhancement and with a minimum

pressure drop penalty. In order to achieve this aim, the following sub objectives are

intended to be achieved:

a) To enhance the heat transfer by utilizing some modified spirally

corrugated tubes. This objective would be achieved by testing different

corrugation height to diameter e/d and corrugation pitch to diameter p/d

to produce swirl secondary flow and boundary layer, which means more

heat transfer

b) To simulate a double, triple and multiple corrugations starts of circular

profile by using commercial CFD software for the tube to increase heat

transfer and decrease pressure drop, while a single smooth tube of

certain specifications will be employed in experiments for validation

purposes.

c) To determine the thermal performance factor (η) for each tube. In

addition, to determine the number of start N effects on both heat transfer

and pressure drop.

8

1.6. Scope of Research

This study shall focus on the followings:

a) Laminar forced convective heat transfer of a Newtonian fluid flow in

spirally corrugated tubes will be considered.

b) Water will be taken as a working fluid and the flow will be assumed as

steady and incompressible. The fluid properties such as viscosity μ, heat

capacity cp and thermal conductivity k will be taken as a function of

temperature.

c) The investigation will be carried out numerically and experimentally

under a constant wall heat flux condition for 100<Re<1300 and for

various geometrical parameters in order to get wide range of database.

1.7. Significance and Contributions of this Study

The current study focused on laminar flow of water in corrugated tubes to

enhance the heat transfer rate because there is a lack in the experimental studies

concerning this subject in the literature as depicted in the next chapter in Section 2.4.

In addition, there are only three authors whom proposed correlations of

Nusselt number and friction factor for the laminar flow of water in annuli or fluted

tubes without taking the effect of severity index in to the account, and there is no

correlations regarding the corrugated tube.

9

1.8. Organization of the Thesis

This thesis consist of six chapters, each one deals with specific aspect.

Chapters (1-2) provide a general introduction and thesis headlines, in addition to the

deep and comprehensive review of the problem. While Chapters (3-5) provide the

detailed methodology and tools to investigate and solve the problem. Chapter 6

presents the outcomes and its interpretations.

Chapter 1 presents the general information about the problem and it is nature,

as well problem background. In addition, the motivation behind the need of the

current investigation and close scope on the problem with its limitations.

Chapter 2 involved the literature review and the research that conducted in

the past which are related to the current investigation research. It shows a

comprehensive and criticized review of about 95% of studies concerned with heat

transferred by corrugation. In addition it contains the summary of all the related

studies.

Chapter 3 depicts and describes the experimental methodology of the

research. Hence, it consists of the experimental rig description, experimental

procedure, experimental measurements and instrument calibration.

Chapter 4 explains the mathematical modelling and simulation steps. It’s also

explained in details the modeling of the problem besides the validation and

verification of the simulation process. The number and characteristics of the

numerically tested tubes were also depicted in this chapter. In addition to the mesh

process and convergence criteria.

10

Chapter 5 shows the results and their discussions. It also shows the effect of

different parameters that have significant effects on the results with reasonable

explanations. This chapter also presents the extracted correlations for the heat

transfer and friction factor.

183

REFERENCES

1. Adachi, T., and Uehara, H. Correlation between heat transfer and pressure

drop in channel with periodically grooved parts. International Journal of

Heat and Mass Transfer, 2001. 44:4333-4343.

2. Patil, S.V., Babu, P.V.V., 2011. Heat transfer augmentation in a circular

tube and square duct fitted with swirl flow generators: a review.

International Journal of Chemical Engineering and Applications, 2, 326–

331.

3. Elshafei. E. A. M., Mohamed. M. S., Mansour. H. and Sakr. M.

Experimental study of heat transfer in pulsating turbulent flow in a pipe.

International Journal of Heat and Fluid Flow, 2008. 29: 1029-38.

4. Bergles. A. E. and Newell Jr. P. H. The influence of ultrasonic vibrations

on heat transfer to water flowing in annuli. International Journal of Heat

Mass Transfer, 1965. 8: 1273-1280.

5. Volk, J. Enhancing Heat Transport through Oscillatory Flows. Ph.D.

Thesis. University of Florida; 2006

6. Gül. H. Heat transfer in oscillating circular pipes. Experimental Heat

Transfer, 2007. 20: 73–84, 2007.

7. Pendyala. R., Jayanti. S. and Balakrishnan. A. R. Convective heat transfer

in single-phase flow in a vertical tube subjected to axial low frequency

oscillations. Heat Mass Transfer, 2008. 44: 857-864.

8. Gül. H. Experimental investigation on the heat transfer of turbulent flow in

a pipe oscillating at low frequencies. Experimental Heat Transfer, 2008.

21: 24–37.

184

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